WO2019054510A1 - Pompe hydraulique - Google Patents

Pompe hydraulique Download PDF

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Publication number
WO2019054510A1
WO2019054510A1 PCT/JP2018/034305 JP2018034305W WO2019054510A1 WO 2019054510 A1 WO2019054510 A1 WO 2019054510A1 JP 2018034305 W JP2018034305 W JP 2018034305W WO 2019054510 A1 WO2019054510 A1 WO 2019054510A1
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WO
WIPO (PCT)
Prior art keywords
axial direction
actuator
oil
movable body
piston
Prior art date
Application number
PCT/JP2018/034305
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English (en)
Japanese (ja)
Inventor
藤井規臣
西谷拓也
中井雅也
Original Assignee
アイシン・エィ・ダブリュ株式会社
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Filing date
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Application filed by アイシン・エィ・ダブリュ株式会社 filed Critical アイシン・エィ・ダブリュ株式会社
Publication of WO2019054510A1 publication Critical patent/WO2019054510A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid

Definitions

  • the present invention relates to a hydraulic pump including an actuator and a pump unit driven by the actuator to generate hydraulic pressure.
  • Patent Document 1 describes an electromagnetic pump (20) including a solenoid unit (30) as an actuator for driving the pump unit (40).
  • the solenoid unit (30) moves the piston (60) of the pump unit (40) forward by attracting the plunger (34) to the core (36) by the electromagnetic force generated in the electromagnetic coil (32). It is configured.
  • the electromagnetic pump (20) is operated by moving the piston (60) forward by the electromagnetic force of the solenoid unit (30) and moving the piston (60) backward by the biasing force of the coil spring (46). It is configured to pump oil.
  • the discharge flow rate of oil by the hydraulic pump corresponds to the stroke amount of the piston (movement amount of the piston along the axial direction of the cylinder) and the stroke number of the piston per unit time It becomes settled.
  • the stroke amount of the piston increases, the volume change amount of the pressure chamber (pump chamber) accompanying the reciprocation of the piston increases, and the oil discharge amount accompanying one reciprocation of the piston increases.
  • the number of strokes of the piston per unit time increases, the number of times of oil discharge per unit time increases.
  • a hydraulic pump is a hydraulic pump including an actuator and a pump unit driven by the actuator to generate hydraulic pressure
  • the pump unit includes a cylinder having an inlet and an outlet.
  • a piston disposed in a pressure chamber formed in the interior of the cylinder so as to communicate with the suction port and the discharge port, and reciprocating in the axial direction of the cylinder;
  • the actuator includes the cylinder A cylindrical coil body coaxially arranged in the axial direction, and being connected to the piston and disposed so as to overlap with the cylindrical coil body in a radial direction along the radial direction of the cylinder, And a movable body capable of reciprocating in the axial direction with respect to the cylindrical coil body, wherein the movable body is movable in the axial direction by magnetic flux generated from the cylindrical coil body. It is driven toward the side.
  • the actuator for driving the pump unit is configured to drive the movable body toward both sides in the axial direction by the magnetic flux generated from the cylindrical coil body. Therefore, the stroke amount of the movable body capable of appropriately generating thrust can be increased compared to the case where the movable body is driven only toward one side in the axial direction by the magnetic flux generated from the cylindrical coil body. Easy to configure the actuator. Therefore, the stroke amount of the piston, which is determined according to the stroke amount of the movable body, can be easily increased to such an extent that a desired discharge flow rate can be obtained. As described above, according to the above configuration, the stroke amount of the piston can be easily increased to such an extent that a desired discharge flow rate can be obtained, so that the discharge flow rate of oil can be easily secured appropriately.
  • Sectional view of hydraulic pump with piston in center of range of motion Cross section of hydraulic pump with piston at one end of range of motion
  • Sectional view of hydraulic pump with piston at other end of range of motion Characteristic chart showing the relationship between angular frequency ratio and amplitude ratio
  • Schematic diagram of the case Diagram showing an example of a drive circuit Diagram showing a drive circuit according to a comparative example
  • the external space 6 corresponds to "the space outside the actuator”
  • the first wall 61 corresponds to the "axial first side wall of the intermediate chamber”
  • the second wall 62 corresponds to "the intermediate chamber
  • the first seal member S1 corresponds to a "sealing member”.
  • the hydraulic pump 1 includes an actuator 2 and a pump unit 3 driven by the actuator 2 to generate an oil pressure. Further, as shown in FIG. 5, the hydraulic pump 1 includes a control unit 90 that controls the drive of the pump unit 3 by the actuator 2.
  • the pump unit 3 is a piston pump that pumps oil by reciprocating the piston 40 along the axial direction DL (axial direction of the cylinder 30), and the actuator 2 is connected to the piston 40 A thrust for moving the movable body 20 along the axial direction DL is generated. That is, the actuator 2 is a linear actuator.
  • the actuator 2 is an electromagnetic actuator that generates a thrust of the movable body 20 by an electromagnetic force.
  • the pump unit 3 includes a cylinder 30 having an inlet 31 and an outlet 32 and a piston 40 that reciprocates along the axial direction DL.
  • a pressure chamber 33 is formed in the cylinder 30 so as to communicate with the suction port 31 and the discharge port 32, and the piston 40 is disposed in the pressure chamber 33.
  • the oil 83 (see FIG. 5) sucked into the pressure chamber 33 from the suction port 31 is discharged from the discharge port 32 to the outside of the pressure chamber 33.
  • a suction oil passage 85 is connected to the suction port 31 and a discharge oil passage 86 is connected to the discharge port 32 (see also FIG. 1).
  • the suction port 31 is disposed so as to suction the oil 83 stored in the oil storage portion 82.
  • the cylinder 30 includes a cylindrical portion 34 formed in a cylindrical shape (here, cylindrical shape) extending in the axial direction DL, and the pressure chamber 33 has an inner periphery of the cylindrical portion 34. It is formed surrounded by a surface (inner wall).
  • the suction port 31 is formed at the opening of one side of the cylindrical portion 34 in the axial direction DL (the first side DL1 in the axial direction described later), and the discharge port 32 is a peripheral wall portion of the cylindrical portion 34 Is formed to penetrate in the radial direction DR (the radial direction of the cylinder 30). That is, the discharge port 32 is provided to communicate the inner peripheral surface and the outer peripheral surface of the cylinder 30 (specifically, the cylindrical portion 34).
  • the side on which the cylinder 30 is disposed with respect to the actuator 2 in the axial direction DL (specifically, the tubular coil body 10 described later) is referred to as an axial first side DL1, and the axial direction first in the axial direction DL
  • the side opposite to the side DL1 is referred to as an axial second side DL2.
  • the piston 40 includes a pressure chamber 33 (pump chamber), a first pressure chamber 33a (first pump chamber) on the first axial side DL1, and a second pressure chamber 33b (second pump chamber) on the second axial side DL2.
  • the first pressure chamber 33 a is formed in communication with the suction port 31
  • the second pressure chamber 33 b is formed in communication with the discharge port 32. That is, the discharge port 32 communicates with the second pressure chamber 33 b.
  • a portion which divides the first pressure chamber 33a and the second pressure chamber 33b in the piston 40 is referred to as a main body portion 41.
  • the space between the outer peripheral surface of the main body 41 and the inner peripheral surface of the cylinder 30 (specifically, the cylindrical portion 34) is A second seal member S2 (annular seal member) that seals is provided on the outer peripheral surface of the main body portion 41.
  • the first pressure chamber 33a and the second pressure chamber 33b are partitioned in an oil-tight manner in a state where a second check valve V2 described later is closed.
  • a first through hole 61a penetrating in the direction DL is formed, and the piston 40 has a first portion 51 arranged to penetrate the first through hole 61a.
  • the first portion 51 and the main body portion 41 are both formed to have a cylindrical (here, cylindrical) outer peripheral surface extending in the axial direction DL, and the outer peripheral surface of the first portion 51 is the outer peripheral surface of the main body 41 It has a smaller diameter than that. Therefore, as shown in FIGS.
  • the volume of the second pressure chamber 33b increases as the piston 40 moves to the first axial side DL1, and decreases as the piston 40 moves to the second axial side DL2.
  • the volume of the first pressure chamber 33a decreases as the piston 40 moves to the first axial side DL1, and increases as the piston 40 moves to the second axial side DL2.
  • the piston 40 includes the main body 41 and the first portion 51.
  • the main-body part 41 divides the pressure chamber 33 into the 1st pressure chamber 33a and the 2nd pressure chamber 33b adjacent to axial direction 2nd side DL2 with respect to the 1st pressure chamber 33a.
  • the first portion 51 defines the second pressure chamber 33 b and an intermediate chamber 60 described later.
  • a first check valve V1 is provided to restrict the flow of the oil 83 (that is, the flow of the oil 83 toward the upstream side).
  • the first check valve V1 is provided at the suction port 31.
  • the first check valve V1 includes a spherical valve body and a biasing member that biases the valve body in the valve closing direction.
  • the first check valve V1 has a predetermined hydraulic pressure (the above-described urging) than the hydraulic pressure on the upstream side (here, the hydraulic pressure of the suction oil passage 85) is lower than the hydraulic pressure on the downstream side (here, the hydraulic pressure of the first pressure chamber 33a). It is configured to open when the oil pressure corresponding to the biasing force of the member is higher than the above) and to close the valve otherwise.
  • the flow path of the oil 83 between the first pressure chamber 33a and the second pressure chamber 33b is allowed.
  • a second check valve V2 for restricting the flow of the oil 83 directed to the opposite side that is, the flow of the oil 83 directed to the upstream side.
  • the flow path of the oil 83 between the first pressure chamber 33a and the second pressure chamber 33b is formed by a hole that penetrates the piston 40 (specifically, the main body 41) in the axial direction DL.
  • the second check valve V2 is provided integrally with the piston 40 (specifically, the main body 41).
  • the second check valve V2 is built in the piston 40.
  • the second check valve V2 includes a spherical valve body and a biasing member that biases the valve body in the valve closing direction.
  • the second check valve V2 has a predetermined hydraulic pressure (above: the hydraulic pressure of the first pressure chamber 33a here) than the hydraulic pressure of the downstream side (here, the hydraulic pressure of the second pressure chamber 33b). It is configured to open when the oil pressure is higher than the hydraulic pressure corresponding to the biasing force of the biasing member, and to close the valve otherwise.
  • 1st non-return valve V1 and the 2nd non-return valve V2 are made into a valve which has a spherical valve body here, as a 1st non-return valve V1 or the 2nd non-return valve V2, a poppet valve etc.
  • Other construction valves may be used.
  • the pump unit 3 is configured as described above, when the piston 40 moves to the second axial side DL2 in the axial direction as shown in FIG. 3, the volume of the first pressure chamber 33a increases, so that the hydraulic pressure of the first pressure chamber 33a is increased. As the volume of the second pressure chamber 33b decreases, the hydraulic pressure of the second pressure chamber 33b rises. Along with this, the first check valve V1 is opened and the second check valve V2 is closed, and the oil 83 of the suction oil passage 85 flows into the first pressure chamber 33a from the suction port 31, and The oil 83 in the pressure chamber 33b is discharged from the discharge port 32 to the discharge oil passage 86 (see also FIG. 5). Further, as shown in FIG.
  • the actuator 2 is a cylindrical coil body 10 coaxially arranged with the cylinder 30 in the axial direction DL, and a movable body capable of reciprocating in the axial direction DL with respect to the cylindrical coil body 10 It has 20 and.
  • the cylindrical coil body 10 is disposed on the second axial side DL2 with respect to the cylinder 30.
  • the movable body 20 is coupled to the piston 40.
  • the movable body 20 is coupled to the piston 40 from the second axial direction DL2 so as to move in the axial direction DL integrally with the piston 40.
  • the movable body 20 is disposed so as to overlap the cylindrical coil body 10 in a radial direction along the radial direction DR.
  • the movable body 20 is disposed radially inward of the cylindrical coil body 10 (inside of the radial direction DR). That is, the movable body 20 is configured to reciprocate along the axial direction DL in a space surrounded by the cylindrical coil body 10 from the radial outer side DR2 (the outer side of the radial direction DR).
  • the cylindrical coil body 10 includes a core 12 formed in a cylindrical shape (here, a cylindrical shape) extending in the axial direction DL, and a coil 11 wound around the core 12.
  • the coil 11 is cylindrically wound around the axis of the core 12, and the cylindrical coil body 10 generates a magnetic flux for driving the movable body 20 in the axial direction DL in a state where the coil 11 is energized.
  • the cylindrical coil body 10 is provided with the coil 11 which generate
  • the cylindrical coil body 10 includes a plurality of coils 11 arranged in the axial direction DL.
  • the cylindrical coil body 10 includes two coils 11 (a first coil 11a and a second coil 11b) arranged in the axial direction DL.
  • the two coils 11 adjacent to each other in the axial direction DL flow in current in opposite directions to generate magnetic flux in opposite directions.
  • the two coils 11 adjacent to each other in the axial direction DL are arranged at an interval in the axial direction DL.
  • three magnetic poles of the first magnetic pole 12a, the second magnetic pole 12b, and the third magnetic pole 12c are formed at the end of the radially inner side DR1 of the core 12 sequentially from the axial first side DL1.
  • the first magnetic pole 12 a is formed on a portion of the core 12 which is disposed on the first axial side DL 1 with respect to the first coil 11 a and which extends to the radially inner side DR 1.
  • the second magnetic pole 12 b is formed of the core 12
  • the third magnetic pole 12 c is formed in a portion extending from the portion disposed between the first coil 11 a and the second coil 11 b in the axial direction DL to the radially inner side DR 1, and the third magnetic pole 12 c is a second coil 11 b in the core 12.
  • it is formed in the part extended to radial direction inner side DR1 from the part arrange
  • the magnetic pole 12b is magnetized so as to have an opposite polarity to the first magnetic pole 12a and the third magnetic pole 12c. Therefore, by switching the direction of the current flowing through the first coil 11a and the second coil 11b, the first magnetic pole 12a and the third magnetic pole 12c act as the N pole and the second magnetic pole 12b acts as the S pole. It is switched to the state where the first magnetic pole 12a and the third magnetic pole 12c act as the S pole and the second magnetic pole 12b acts as the N pole.
  • the movable body 20 is driven toward at least one side in the axial direction DL by the magnetic flux generated from the cylindrical coil body 10.
  • the movable body 20 is driven toward both sides in the axial direction DL by the magnetic flux generated from the cylindrical coil body 10.
  • the movable body 20 is driven toward both sides in the axial direction DL by switching the energization direction of the coil 11 of the cylindrical coil body 10. That is, the movable body 20 is driven toward both sides in the axial direction DL by repeating switching of the direction of the current supplied to the cylindrical coil body 10. Since the movable body 20 is connected to the piston 40, the piston 40 reciprocates along the axial direction DL by driving the movable body 20 toward both sides in the axial direction DL.
  • the movable body 20 is provided with a permanent magnet M.
  • the permanent magnet M is provided on the movable body 20 in such a manner that the thrust of the movable body 20 can be obtained by the interaction between the magnetic flux generated from the permanent magnet M and the magnetic flux generated from the cylindrical coil body 10.
  • the movable body 20 includes the shaft member 21 extending in the axial direction DL, and the permanent magnet M formed in a cylindrical shape (here, a cylindrical shape) coaxial with the shaft member 21 is the shaft member 21. It is fixed to the outer peripheral surface of.
  • permanent magnet M is magnetized by radial direction DR.
  • the movable body 20 includes a plurality of permanent magnets M arranged in the axial direction DL.
  • the movable body 20 includes two permanent magnets M (a first permanent magnet M1 and a second permanent magnet M2) arranged side by side in the axial direction DL. That is, the movable body 20 includes the same number of permanent magnets M as the number of the coils 11 provided in the cylindrical coil body 10.
  • Two permanent magnets M adjacent to each other in the axial direction DL are magnetized in opposite directions to each other in the radial direction DR. Further, two permanent magnets M adjacent to each other in the axial direction DL are arranged at an interval in the axial direction DL.
  • the first permanent magnet M1 is disposed to face the first coil 11a in the radial direction DR
  • the two permanent magnets M2 are disposed to face the second coil 11b in the radial direction DR.
  • the first permanent magnet M1 has a portion of the axial first side DL1 facing the first magnetic pole 12a in the radial direction DR and the axial second side DL2 Is disposed so as to face the second magnetic pole 12b in the radial direction DR.
  • the second permanent magnet M2 has a portion on the axial first side DL1 facing the second magnetic pole 12b in the radial direction DR and a portion on the axial second side DL2 Are arranged to face the third magnetic pole 12 c in the radial direction DR.
  • the actuator 2 is configured as described above, when currents flowing in opposite directions flow through the first coil 11a and the second coil 11b, the movable body 20 moves in the axial direction DL by the magnetic flux generated from the cylindrical coil body 10. It is driven toward one side. Further, when the direction of the current flowing through the first coil 11a is reversed and the direction of the current flowing through the second coil 11b is reversed, the movable body 20 is moved to the other side in the axial direction DL by the magnetic flux generated from the cylindrical coil body 10. Drive towards. Therefore, by switching the direction of energization of the coil 11 (here, the first coil 11a and the second coil 11b), the movable body 20 and the piston 40 coupled thereto can be reciprocated along the axial direction DL. it can.
  • the discharge flow rate (discharge amount per unit time) of the oil 83 by the hydraulic pump 1 is the stroke amount of the piston 40 (movement amount of the piston 40 along the axial direction DL) and the stroke number of the piston 40 per unit time It depends on and. Specifically, as the stroke amount of the piston 40 increases, the volume change amount of the pressure chamber 33 accompanying the reciprocation of the piston 40 increases, and the discharge amount of the oil 83 accompanying one reciprocation of the piston 40 increases. Become. Further, as the number of strokes of the piston 40 per unit time increases, the number of times the oil 83 is discharged per unit time increases.
  • the actuator 2 for driving the pump unit 3 drives the movable body 20 toward both sides in the axial direction DL by the magnetic flux generated from the cylindrical coil body 10. Is configured. Therefore, compared with the case where the movable body 20 is driven only to one side in the axial direction DL by the magnetic flux generated from the cylindrical coil body 10, the stroke amount of the movable body 20 capable of appropriately generating thrust.
  • the actuator 2 is easy to configure so that Therefore, the stroke amount of the piston 40, which is determined according to the stroke amount of the movable body 20, can easily be increased to such an extent that a desired discharge flow rate can be obtained.
  • the movable body 20 driven by the magnetic flux generated from the cylindrical coil body 10 includes the permanent magnet M. Therefore, the number of turns of the coil 11 required to obtain a desired thrust can be reduced as compared with the case where the movable body 20 is not provided with the permanent magnet M. Therefore, the inductance of the coil 11 can be reduced to improve the current response of the actuator 2, and as a result, a desired discharge flow rate can be obtained for the drive frequency of the actuator 2 that determines the number of strokes of the piston 40 per unit time. It is easy to raise to some extent.
  • the hydraulic pump 1 is disposed such that the actuator 2 is used in the air environment. Therefore, since the movable body 20 can be reciprocated along the axial direction DL in a space not filled with the oil 83, viscosity and the like of the oil 83 when the movable body 20 reciprocates along the axial direction DL It is possible to keep the resulting sliding resistance small and secure a large stroke amount of the movable body 20.
  • the amount of heat generation of the actuator 2 is large and it is necessary to cool the actuator 2 with the oil 83, it is necessary to use the actuator 2 under the environment in oil, but in the hydraulic pump 1, as described above It is possible to reduce the number of turns of the coil 11 required to obtain a desired thrust. As a result, the amount of heat generation of the actuator 2 can be easily reduced to such an extent that the actuator 2 can be used in the air environment.
  • the pump unit 3 is configured to generate the hydraulic pressure required by the drive device 81 housed in the case 80 as shown in FIG.
  • the driving device 81 is disposed in a housing space 80 a formed inside the case 80.
  • the drive device 81 is, for example, a drive device for a vehicle mounted on a vehicle, such as a stepped or continuously variable automatic transmission, a manual transmission, or a drive transmission device for a hybrid vehicle or an electric vehicle.
  • the driving device 81 is configured to transmit the driving force (torque) between the driving force source of the wheel and the wheel.
  • the drive device 81 includes, for example, a rotating electrical machine as a driving force source of wheels.
  • a hydraulic pressure required for lubrication or cooling of each part of the drive unit 81 is provided as the hydraulic pressure required by the drive unit 81, or the drive unit 81 is provided with a device (such as an engagement device) operated by the hydraulic pressure.
  • the hydraulic pressure required for actuation or preparation for actuation can be illustrated.
  • the oil discharged from the hydraulic pump 1 is supplied to a portion of the drive device 81 requiring oil pressure via the discharge oil passage 86.
  • the oil discharged from the hydraulic pump 1 may be supplied to a portion of the drive device 81 that requires the hydraulic pressure after the hydraulic pressure is controlled by a hydraulic control device (not shown).
  • the pump unit 3 (specifically, the suction port 31, see FIG. 1) is configured to suck the oil 83 stored in the oil storage unit 82 inside the case 80. It is located inside.
  • the oil reservoir 82 is formed at the bottom of the case 80, and the suction port 31 is arranged to suction the oil 83 stored in the oil reservoir 82 via the suction oil passage 85.
  • the actuator 2 is disposed outside the case 80, which makes it possible to use the actuator 2 in the air environment.
  • the actuator 2 is disposed outside the case 80 means that at least a part of the actuator 2 (at least a portion of the second side DL2 in the axial direction) is disposed outside the case 80, A part (a part of the axial direction first side DL1) may be disposed inside the case 80. That is, at least a part of the actuator 2 is disposed outside the case 80.
  • positioned by the direction which the axial direction DL follows a horizontal surface is illustrated.
  • the case where the actuator 2 is used in the air environment by disposing the actuator 2 outside the case 80 has been exemplified, but in the inside of the case 80, the oil surface 84 of the oil reservoir 82 is used.
  • the actuator 2 may be configured to be used in an air environment or an environment close to the air environment by disposing the actuator 2 above (above the vertical direction Z).
  • the vertical direction Z means the vertical direction when the hydraulic pump 1 is in use, and here means the vertical direction when the case 80 is mounted on a vehicle.
  • At least a part of the pump unit 3 (for example, the suction port 31) may be disposed below the oil surface 84 of the oil reservoir 82 (downward in the vertical direction Z).
  • the oil level 84 of the oil reservoir 82 is, for example, the highest oil level within the range of change of the oil level 84 of the oil reservoir 82, or the hydraulic pump 1 is in operation and the oil level of the hydraulic pump 1 is The oil surface 84 of the oil reservoir 82 in a stable state can be obtained.
  • the actuator 2 is disposed outside the case 80, and both the actuator 2 and the pump unit 3 are disposed above the oil surface 84 of the oil reservoir 82.
  • the oil of the pressure chamber 33 further infiltrates into the facing portion 2 a where the cylindrical coil body 10 and the movable body 20 oppose in the radial direction DR, and the sliding of the movable body 20
  • an oil blocking structure 5 is provided between the opposing portion 2a and the pressure chamber 33 in the axial direction DL to block the entry of oil 83 from the pressure chamber 33.
  • the oil shutoff structure 5 includes an intermediate chamber 60 partitioned between the pressure chamber 33 and the pressure chamber 33 in an oil-tight manner using the first seal member S1 between the pressure chamber 33 and the actuator 2 in the axial direction DL. Have. That is, the intermediate chamber 60 is partitioned from the pressure chamber 33. The intermediate chamber 60 is provided between the pressure chamber 33 and the facing portion 2 a of the actuator 2 in the axial direction DL.
  • the first wall 61 which is a wall of the first axial side DL1 of the intermediate chamber 60 is formed by the cylinder 30 (specifically, the cylindrical portion 34), and the first wall 61 of the cylinder 30
  • a first through hole 61 a through which the first portion 51 of the piston 40 passes is formed in a portion forming the portion 61.
  • the outer peripheral surface of the first portion 51 and the inner peripheral surface of the first through hole 61a are formed to divide the pressure chamber 33 (specifically, the second pressure chamber 33b) and the intermediate chamber 60 in an oil tight manner.
  • a first seal member S1 annular seal member for sealing the gap is provided on the outer peripheral surface of the first portion 51.
  • the second wall 62 which is a wall of the axial second side DL 2 of the intermediate chamber 60 is formed by the cylindrical coil body 10 (specifically, the core 12), and the second wall 62 in the cylindrical coil body 10 In the portion forming the wall 62, a second through hole 62a through which the second portion 52 of the movable body 20 penetrates is formed.
  • the second portion 52 of the movable body 20 is connected to the first portion 51 of the piston 40 at the intermediate chamber 60. That is, the connecting portion 53 between the first portion 51 and the second portion 52 is disposed in the intermediate chamber 60.
  • Each of the first portion 51 and the second portion 52 is formed to have a cylindrical (here, cylindrical) outer peripheral surface extending in the axial direction DL.
  • a first closing member B1 (here, a portion between the inner circumferential surface of the second through hole 62a and the outer circumferential surface of the second portion 52).
  • Bush is arranged between the second through hole 62a and the second portion 52.
  • "occluding” means closing at least a portion of the gap.
  • the third wall 63 which is a wall of the radially outer side DR2 of the intermediate chamber 60 is formed by the cylindrical coil body 10 (specifically, the core 12).
  • the discharge port 7 penetrating the part in the radial direction DR is formed. That is, the intermediate chamber 60 is opened to the external space 6 which is the space outside the actuator 2 through the discharge port 7.
  • the discharge port 7 is arrange
  • the third wall 63 may be formed of a member (for example, a cylinder 30) different from the cylindrical coil body 10, and the discharge port 7 may be provided in a portion of the member where the third wall 63 is formed.
  • the intermediate chamber 60 is provided between the pressure chamber 33 (specifically, the second pressure chamber 33 b) and the actuator 2 (the facing portion 2 a) in the axial direction DL, and 60 is oil-tightly partitioned from the pressure chamber 33 using the first seal member S1.
  • the first seal member S1 can regulate the oil 83 from leaking from the pressure chamber 33 to the axial second side DL2, and even if such an oil 83 leaks, It is possible to cause the oil 83 to flow into the intermediate chamber 60 instead of the inside of the actuator 2 (the facing portion 2a).
  • the intermediate chamber 60 is opened to the external space 6, even if the oil 83 flows into the intermediate chamber 60, the oil 83 is not contained in the inside of the actuator 2 (facing portion It is possible to discharge to the external space 6 without flowing into 2a), that is, to block the entry of the oil 83 into the inside (the facing portion 2a) of the actuator 2.
  • the outer peripheral surface of the first portion 51 and the outer peripheral surface of the second portion 52 are formed to have the same diameter.
  • the variation of the pressure in the intermediate chamber 60 can be reduced, and the pressure difference between the intermediate chamber 60 and the inside of the actuator 2 (opposite portion 2a) can be kept small.
  • 83 is configured to be hard to infiltrate into the inside of the actuator 2 (opposite portion 2a).
  • the diameters of the outer peripheral surface of the first portion 51 and the outer peripheral surface of the second portion 52 may be different, even in this case, the outer peripheral surface of the first portion 51 and the second portion 52 It is preferable to minimize the difference in diameter with the outer peripheral surface as much as possible and to minimize the volume change of the intermediate chamber 60 as much as possible.
  • the structure of the oil blocking structure 5 shown here is an example, and it is possible to change the structure of the oil blocking structure 5 suitably.
  • the hydraulic pump 1 may not be provided with the oil shutoff structure 5.
  • the first closing member B1 is disposed between the second through hole 62a and the second portion 52.
  • the actuator 2 is configured such that the third portion 23, which is a portion of the second side DL2 in the axial direction than the second portion 52 of the movable body 20, is inserted into the second side DL2 in the axial direction than the second through hole 62a.
  • a third through hole 13 is provided, and the second through hole 13 is closed between the inner peripheral surface of the third through hole 13 and the outer peripheral surface of the third portion 23 between the third through hole 13 and the third portion 23.
  • a closing member B2 (here, a bush) is disposed.
  • the third portion 23 is a portion on the second side DL2 in the axial direction of the permanent magnet M (here, the first permanent magnet M1 and the second permanent magnet M2) in the movable body 20.
  • the third portion 23 constitutes an end portion of the movable body 20 on the second axial side DL2.
  • the third portion 23 is smaller in diameter than the third portion 23 of the movable body 20 than the portion on the first axial side DL1 (here, the portion provided with the permanent magnet M).
  • the 3rd penetration hole 13 is formed in the end of axial direction 2nd side DL2 in cylindrical coil object 10 (specifically, core 12).
  • the third through hole 13 is a wall of the axial direction second side DL2 of the accommodation chamber of the movable body 20 formed inside the actuator 2 in the cylindrical coil body 10 (specifically, the core 12). It is formed in the part to form.
  • the hydraulic pump 1 has a first biasing member 71 for biasing the piston 40 toward the first axial side DL1, and a second biasing member for biasing the piston 40 toward the second axial side DL2.
  • a biasing member 72 is provided.
  • the first biasing member 71 is provided to bias the piston 40 toward the first axial side DL1 regardless of the position of the piston 40 in the axial direction DL
  • the second biasing member 72 is a piston
  • the piston 40 is provided so as to bias the piston 40 toward the second axial side DL2 regardless of the position of the axial direction DL.
  • the hydraulic pump 1 reciprocates the piston 40 along the axial direction DL by using the resonance phenomenon of the piston 40 by the first biasing member 71 and the second biasing member 72.
  • the first biasing member 71 and the second biasing member 72 are biasing members that bias the piston 40 in the axial direction DL, and function as resonance biasing members for causing the piston 40 to resonate.
  • this hydraulic pump 1 by compensating the thrust generated by the actuator 2 by the resonance phenomenon of the piston 40, it is possible to reduce the energy consumption of the actuator 2 for generating the thrust required of the piston 40. It has become.
  • the first biasing member 71 is disposed on the second side DL2 in the axial direction with respect to the first part 51 of the piston 40, and the first portion 51 in the axial direction first side DL1. It is arranged to be biased.
  • the first biasing member 71 is disposed in the intermediate chamber 60.
  • the first biasing member 71 is provided to exert a biasing force on the piston 40 (specifically, the first portion 51) and the core 12.
  • the first biasing member 71 is formed such that the diameter of the first axial side DL1 is smaller than the diameter of the second axial side DL2.
  • the piston 40 (specifically, the first portion 51) and the core 12 (the first portion 51).
  • the first biasing member 71 so as to apply a biasing force to the second portion 52 and the outer portion of the radial direction DR.
  • a coil spring can be used as the first biasing member 71.
  • the first biasing member 71 is disposed in a state in which the expansion and contraction direction follows the axial direction DL and is compressed more than the natural length.
  • the second biasing member 72 is located on the first axial side DL1 with respect to the main body portion 41 of the piston 40 (here, the piston 40 and the first check valve V1 in the axial direction DL ), The body portion 41 is arranged to be biased toward the second axial side DL2.
  • the second biasing member 72 is disposed in the first pressure chamber 33a.
  • the second biasing member 72 is opposite to the piston 40 (specifically, the main body 41) inside the pressure chamber 33 and the side of the actuator 2 in the axial direction DL of the cylinder 30 (ie, An urging force is applied to the end of the first axial side DL1).
  • a coil spring can be used as the second biasing member 72.
  • the second biasing member 72 is disposed in a state in which the expansion and contraction direction follows the axial direction DL and is compressed more than the natural length.
  • the first biasing member 71 and the second biasing member 72 are disposed separately on at least a part of the piston 40 on both sides in the axial direction DL. Specifically, the first biasing member 71 and the second biasing member 72 are divided into both sides in the axial direction DL with respect to the main body portion 41, the first portion 51, and the portion therebetween in the piston 40. Are arranged. And in this embodiment, the 1st biasing member 71 and the 2nd biasing member 72 are arrange
  • both the first biasing member 71 and the second biasing member 72 are disposed so as not to inhibit the flow of the oil 83 discharged from the discharge port 32, whereby the flow path resistance at the discharge port 32 is obtained. Is kept low.
  • the first biasing member 71 is disposed in the intermediate chamber 60
  • the second biasing member 72 is disposed in the first pressure chamber 33a
  • the discharge port 32 is provided in communication with the second pressure chamber 33b.
  • the first urging member 71 and the second urging member 72 do not overlap with the discharge port 32 in the radial direction.
  • the actuator 2 is configured to reciprocate the movable body 20 along the axial direction DL at a set drive frequency. That is, the control unit 90 is configured to control the actuator 2 such that the movable body 20 reciprocates along the axial direction DL at the set drive frequency.
  • the control unit 90 is configured to control the actuator 2 via a drive circuit (specifically, a single-phase inverter circuit) which is not shown.
  • the control unit 90 controls the drive circuit such that an AC voltage having a set drive frequency is applied to the actuator 2 (specifically, the coil 11).
  • the drive frequency of the actuator 2 is set according to the diameter of the piston 40 and the stroke amount of the piston 40 so as to obtain the required discharge flow rate of the oil 83.
  • the drive frequency of the actuator 2 is set so as to obtain a target discharge flow rate corresponding to the required flow rate of the automatic transmission which is determined according to the traveling state of the vehicle (for example, at the time of shifting, steady traveling etc.).
  • the vibration system including the piston 40, the first biasing member 71, and the second biasing member 72 becomes in a resonant state as the movable body 20 reciprocates, so that the first biasing member 71 and the second biasing member
  • the combined spring constant with the biasing member 72 is set based on the drive frequency.
  • the vibration system including the piston 40, the first biasing member 71, and the second biasing member 72 has an axis at the movable body 20 at a driving frequency at which the resonant state occurs as the movable body 20 reciprocates. Reciprocate along the direction DL.
  • the pump unit 3 (specifically, the movable body 20) is driven at a drive frequency that can ensure the target discharge flow rate of the pump unit 3 (the target discharge flow rate of the hydraulic pump 1).
  • the vibration system also includes the movable body 20.
  • the drive frequency of the actuator 2 is set to be variable, the drive frequency for setting the combined spring constant can be, for example, the drive frequency with the highest frequency of use.
  • the equation of motion of the piston 40 in the hydraulic pump 1 can be expressed by the equation of motion of damped forced vibration as described below.
  • the mass of the entire movable portion 4 that reciprocates along the axial direction DL at the drive frequency, including the piston 40 and the movable body 20 A value obtained by multiplying the target mass (W) by the square of the angular frequency ( ⁇ ) corresponding to the drive frequency as the combined spring constant (K) of the first biasing member 71 and the second biasing member 72 as a mass Is set as the standard.
  • "setting a certain value as a reference” is a concept including both setting to the value and setting the value to the adjusted value.
  • the synthetic spring constant of the 1st energizing member 71 and the 2nd energizing member 72 makes the reference value the value which multiplied the object mass to the square of the angular frequency (driving angular frequency) according to driving frequency. It is set to a reference value or set to a value obtained by adjusting the reference value. In the latter case, for example, from the angular frequency ⁇ 0 represented by the following equation (8) of the actual resonant angular frequency of the vibration system including the piston 40, the first biasing member 71, and the second biasing member 72.
  • the combined spring constant of the first biasing member 71 and the second biasing member 72 can be set to a value obtained by adjusting the above-mentioned reference value, in consideration of the deviation of the above.
  • the equation of motion of the piston 40 will be described.
  • the entire mass of the movable part 4 is W
  • the thrust is F m
  • the hydraulic pressure is P
  • the pressure receiving area of the piston 40 is S
  • the first bias Assuming that the synthetic spring constant of the member 71 and the second biasing member 72 is K and the displacement of the piston 40 is x, the equation of motion of the piston 40 can be expressed by the following equation (1) using a code function sgn.
  • circuit equation of the electric circuit regarding energization to the coil 11 is represented by the following equation (2) with voltage V, electric resistance of the circuit R, current I, inductance of the circuit L and back electromotive force constant k e Be done.
  • Equation (6) is an equation of motion of damped forced vibration, and this equation of motion has a steady-state vibration solution as shown by the following Equation (7) and Equation (8).
  • FIG. 4 is a characteristic diagram showing the relationship between the angular frequency ratio ( ⁇ / ⁇ 0 ) and the amplitude ratio (X a / X s ).
  • the combined spring constant of the first biasing member 71 and the second biasing member 72 is set to the square of the driving angular frequency, and the target mass (the entire movable portion 4 is Is set based on the value obtained by multiplying the mass of
  • the sum of the spring constant of the first biasing member 71 and the spring constant of the second biasing member 72 is the combined spring constant K of the first biasing member 71 and the second biasing member 72.
  • the spring constant of the first biasing member 71 and the spring constant of the second biasing member 72 can be set to the same value (that is, a half value of the combined spring constant K).
  • the spring constant of the first biasing member 71 and the spring constant of the second biasing member 72 may be made different from each other so that the total of these spring constants is the above-described synthetic spring constant K. .
  • the hydraulic pump 1 is provided with two resonance biasing members (71, 72) for biasing the piston 40 to opposite sides in the axial direction DL as a resonance biasing member for generating a resonance phenomenon. ) Is provided. Therefore, compared with the case where only one resonance biasing member is provided, it is easy to secure a large spring constant of the entire vibration system.
  • the stroke amount of the piston 40 which is determined according to the stroke amount of the movable body 20, can be easily increased to such an extent that a desired discharge flow rate can be obtained.
  • the driving frequency of the actuator 2 for determining the number of strokes can be easily increased to such an extent that a desired discharge flow rate can be obtained.
  • a hydraulic pump hereinafter referred to as “electric oil pump” that uses an AC rotating electrical machine driven by AC power (for example, three-phase AC power) of multiple phases as a driving power source of the pump unit.
  • the hydraulic pump 1 also has an advantage of being able to realize the same discharge flow rate as the electric oil pump at lower cost.
  • the actuator 2 used in the hydraulic pump 1 can reduce the number of coils and the number of permanent magnet poles compared to the AC rotating electric machine used in the electric oil pump, the cost can be reduced. .
  • the hydraulic pump 1 can be driven by the drive circuit of single phase. It is possible to reduce the Describing the specific example, the drive circuit 91 of the actuator 2 used in the hydraulic pump 1 is configured using, for example, an inverter circuit as illustrated in FIG.
  • the drive circuit 91 of the rotary electric machine MG used in the electric oil pump is configured using an inverter circuit as illustrated in FIG. 7.
  • the rotary electric machine MG is a rotary electric machine driven by three-phase alternating current, and the rotary electric machine MG includes phase coils 93 corresponding to each of the three phases.
  • the number of switching elements 92 provided in the drive circuit 91 can be reduced to a small number, so that the drive circuit 91 can be simplified.
  • the configuration in which the first biasing member 71 is disposed in the intermediate chamber 60 has been described as an example.
  • the first biasing member 71 may be configured to be disposed at a position different from that of the intermediate chamber 60.
  • the first biasing member 71 may be disposed in the second pressure chamber 33 b to bias the main body 41 of the piston 40 toward the first axial side DL1.
  • one of the first biasing member 71 and the second biasing member 72 (specifically, the first biasing member 71) overlaps the discharge port 32 in the radial direction. To be arranged.
  • the first biasing member 71 and the second biasing member 72 have been described as an example of the configuration in which they are disposed so as not to overlap the discharge port 32 in the radial direction.
  • at least one of the biasing member 71 and the second biasing member 72 may be disposed so as to overlap the discharge port 32 in the radial direction.
  • the second biasing member 72 may be disposed in the intermediate chamber 60.
  • the second biasing member 72 is disposed in the intermediate chamber 60 in a state of being extended more than the natural length, and pivots the first portion 51 of the piston 40. It can be made to urge to direction 2nd side DL2.
  • the intermediate chamber 60 for blocking the entry of the oil 83 into the opposing portion 2a. Can be used effectively.
  • both the first biasing member 71 and the second biasing member 72 may be disposed at positions different from the intermediate chamber 60.
  • the configuration in which the actuator 2 is used in or near an air environment has been described as an example.
  • the configuration in which the actuator 2 is used in an oil environment that is, at least a part of the actuator 2 is disposed below the oil surface 84 of the oil reservoir 82 It can also be configured. In such a case, the hydraulic pump 1 may not be provided with the oil shutoff structure 5.
  • the configuration has been described as an example in which the movable body 20 includes the permanent magnet M magnetized in the radial direction DR.
  • the movable body 20 includes the permanent magnet M magnetized in the axial direction DL, or the permanent magnet M magnetized in the radial direction DR.
  • a permanent magnet M which is magnetized in the axial direction DL.
  • the configuration in which the movable body 20 is disposed at the radially inner side DR1 with respect to the cylindrical coil body 10 has been described as an example. However, without being limited to such a configuration, the movable body 20 may be disposed at the radially outer side DR2 with respect to the cylindrical coil body 10.
  • the resonance biasing member for biasing the piston 40 in the axial direction DL to resonate the piston 40 in the hydraulic pump 1 the first biasing member 71 and the second biasing are used.
  • the configuration in which the member 72 is provided has been described as an example. However, without being limited to such a configuration, the hydraulic pump 1 may be configured to be provided with only one resonance biasing member.
  • the piston 40 when the piston 40 moves to the first axial side DL1 in the axial direction, the piston 40 is urged to the second axial side DL2 in the axial direction, and when the piston 40 moves to the second axial side DL2 in the axial direction
  • the spring constant of the resonance biasing member may be set to the same value as the combined spring constant in the above embodiment.
  • the resonance biasing member is provided to bias the piston 40 in the axial direction DL, but the resonance biasing member moves the movable body 20 in the axial direction DL. It may be provided to bias.
  • the hydraulic pump 1 may not be provided with a resonance biasing member, and the piston 40 may be reciprocated along the axial direction DL with only the thrust generated by the actuator 2.
  • the configuration in which the movable body 20 includes the permanent magnet M has been described as an example.
  • the movable body 20 can be configured not to include the permanent magnet M without being limited to such a configuration. In this case, for example, a state in which only the first coil 11a of the first coil 11a and the second coil 11b is energized, and a state in which only the second coil 11b of the first coil 11a and the second coil 11b is energized
  • the movable body 20 can be configured to be driven toward both sides in the axial direction DL.
  • a hydraulic pump (1) comprising an actuator (2) and a pump unit (3) driven by the actuator (2) to generate hydraulic pressure, the pump unit (3) having a suction port (31) And a pressure chamber (33) formed in the cylinder (30) so as to communicate with the cylinder (30) having the discharge port (32) and the suction port (31) and the discharge port (32).
  • a piston (40) disposed in the axial direction (DL) of the cylinder (30), the actuator (2) being coaxial with the cylinder (30) in the axial direction (DL) And a cylindrical coil body (10) connected to the piston (40) and viewed in a radial direction along a radial direction (DR) of the cylinder (30).
  • the movable body (20) is disposed and reciprocable in the axial direction (DL) with respect to the cylindrical coil body (10), and the movable body (20) is the cylindrical coil body (10). Driven by the magnetic flux generated from) in the axial direction (DL).
  • the actuator (2) for driving the pump portion (3) drives the movable body (20) to both sides in the axial direction (DL) by the magnetic flux generated from the cylindrical coil body (10) Configured as. Therefore, compared with the case where the movable body (20) is driven only to one side in the axial direction (DL) by the magnetic flux generated from the cylindrical coil body (10), the thrust can be generated appropriately.
  • the actuator (2) is easy to configure so that the stroke amount of the movable body (20) becomes large. Therefore, the stroke amount of the piston (40), which is determined according to the stroke amount of the movable body (20), can be easily increased to such an extent that a desired discharge flow rate can be obtained. As described above, according to the above configuration, the stroke amount of the piston (40) can be easily increased to such an extent that a desired discharge flow rate can be obtained, so that the discharge flow rate of the oil (83) can be easily secured appropriately.
  • the movable body (20) includes a permanent magnet (M).
  • the number of turns of the coil is increased because the solenoid has a structure in which the plunger is attracted by the electromagnetic force generated in the coil.
  • the current response of the solenoid decreases because the inductance of the coil increases, and the drive frequency of the solenoid that determines the number of strokes of the piston per unit time can be increased to such an extent that a desired discharge flow rate can be obtained. It can be difficult.
  • produces from a cylindrical coil body (10) is equipped with a permanent magnet (M).
  • the number of turns of the coil (11) included in the cylindrical coil body (10), which is required to obtain a desired thrust, is reduced as compared to the case where the movable body (20) does not include the permanent magnet (M) be able to. Therefore, the inductance of the coil (11) can be reduced to enhance the current response of the actuator (2).
  • the drive frequency of the actuator (2) which determines the number of strokes of the piston (40) per unit time It becomes easy to make it high enough to obtain a desired discharge flow rate.
  • the movable body (20) includes the permanent magnet (M)
  • the switching of the direction of the current supplied to the cylindrical coil body (10) is repeated, thereby the movable body (20) Is preferably driven toward both sides of the axial direction (DL).
  • the movable body (20) can be appropriately driven toward both sides in the axial direction (DL) by repeatedly switching the direction of the current supplied to the cylindrical coil body (10). .
  • the actuator (2) is disposed above the oil level (84) of the oil reservoir (82).
  • the movable body (20) of the actuator (2) can be reciprocated along the axial direction (DL). Therefore, the sliding resistance caused by the viscosity or the like of the oil (83) when the movable body (20) reciprocates along the axial direction (DL) is suppressed small, and the stroke amount of the movable body (20) is secured large. can do.
  • the pump unit (3) generates an oil pressure required by the drive device (81) housed in the case (80), and the suction port (31) stores oil inside the case (80). Disposed inside the case (80) so as to suction oil (83) stored in the part (82), and at least a part of the actuator (2) is disposed outside the case (80) Is preferable.
  • the pump unit (3) when the pump unit (3) generates the hydraulic pressure required by the drive device (81) housed in the case (80), the movable body (20) of the actuator (2) is in the axial direction
  • the space reciprocating along (DL) is likely to be a space substantially free of oil (83). Therefore, the above-described sliding resistance can be suppressed to be small, and a large stroke amount of the movable body (20) can be easily secured.
  • an oil blocking structure (5) is provided between the pressure chambers (33) to block the entry of oil (83) from the pressure chamber (33).
  • the oil shutoff structure (5) is a seal between the pressure chamber (33) and the actuator (2) in the axial direction (DL)
  • the intermediate chamber (60) is provided between the pressure chamber (33) and the actuator (2) in the axial direction (DL), and the intermediate chamber (60) serves as the seal member (S1). It is separated from the pressure chamber (33) in an oil-tight manner. Therefore, the oil (83) can be restricted by the seal member (S1) from leaking from the pressure chamber (33) to the side where the actuator (2) exists in the axial direction (DL), and such oil (temporarily) Even when the leak of 83) occurs, the oil (83) can be made to flow into the intermediate chamber (60) instead of the inside of the actuator (2).
  • the oil blocking structure (5) can appropriately block the entry of the oil (83).
  • the cylinder (30) is disposed with respect to the cylindrical coil body (10) in the axial direction (DL)
  • the movable body (20) has an axially first side (DL1) and a side opposite to the axially first side (DL1) in the axial direction (DL) as an axially second side (DL2).
  • a first through hole (61a) through which the first portion (51) of the piston (40) penetrates is formed in a portion forming the wall (61), and the intermediate chamber (60) in the cylindrical coil body (10) Wall of the second axial side (DL2)
  • a second through hole (62a) through which the second part (52) of the movable body (20) penetrates is formed in the part to be formed, and the connection between the first part (51) and the second part (52)
  • the portion (53) is disposed in the intermediate chamber (60), and the outer peripheral surface of the first portion (51) and the outer peripheral surface of the second portion (52) are formed to have the same diameter. It is.
  • the movable body (20) and the piston (40) are axially (DL)
  • the change in volume of the intermediate chamber (60) can be suppressed to a small level in a state of reciprocating along the direction of the arrow (i.e., at the time of operation of the hydraulic pump (1)).
  • the air pressure difference between the intermediate chamber (60) and the inside of the actuator (2) (opposite portion (2a)) is kept small.
  • the oil (83) present in 60) can be made difficult to infiltrate into the inside (opposite portion (2a)) of the actuator (2).
  • the actuator (2) is closer to the axial second side (DL2) than the second through hole (62a) and the axial direction than the second portion (52) of the movable body (20). It has a third through hole (13) into which a third portion (23) which is a portion of the second side (DL2) is inserted, and between the second through hole (62a) and the second portion (52)
  • the first closing member (B1) is disposed
  • the second closing member (B2) is disposed between the third through hole (13) and the third portion (23).
  • the hydraulic pump which concerns on this indication should just be able to show at least one among each effect mentioned above.
  • Hydraulic pump 2 Actuator 2a: Opposite part 3: Pump part 5: Oil blocking structure 6: External space (space outside the actuator) 10: cylindrical coil body 13: third through hole 20: movable body 23: third portion 30: cylinder 31: suction port 32: discharge port 33: pressure chamber 40: piston 51: first portion 52: second portion 53 : Connection part 60: Intermediate chamber 61: First wall (wall on the axial first side of the intermediate chamber) 61a: first through hole 62: second wall (the second wall on the axial direction of the intermediate chamber) 62a: second through hole 80: case 81: drive device 82: oil reservoir 83: oil 84: oil surface B1: first closing member B2: second closing member DL: axial direction DL1: axial direction first side DL2: Axial second side DR: Radial direction DR1: Radial inside (radial inside) M: permanent magnet S1: first seal member (seal member)

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

La pompe hydraulique (1) de l'invention est équipée d'un vérin (2) et d'une partie pompe (3). La partie pompe (3) est équipée d'un cylindre (30), et d'un piston (40) se déplaçant en va-et-vient suivant une direction axiale (DL). Le vérin (2) est équipé : d'un corps de bobine tubulaire (10) disposé de manière à se ranger dans la direction axiale (DL) de manière coaxiale par rapport au cylindre (30); et d'un corps mobile (20) qui est disposé de manière à la fois à être relié au piston (40) et à se superposer au corps de bobine tubulaire (10) selon une vue de direction radiale suivant une direction radiale (DR), et qui permet de se déplacer en va-et-vient dans la direction axiale (DL) vis-à-vis du corps de bobine tubulaire (10). Le corps mobile (20) est entraîné vers les deux côtés de la direction axiale (DL) sous l'effet d'un flux magnétique généré par le corps de bobine tubulaire (10).
PCT/JP2018/034305 2017-09-15 2018-09-14 Pompe hydraulique WO2019054510A1 (fr)

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JP2017-177939 2017-09-15

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PCT/JP2018/034305 WO2019054510A1 (fr) 2017-09-15 2018-09-14 Pompe hydraulique
PCT/JP2018/034306 WO2019054511A1 (fr) 2017-09-15 2018-09-14 Pompe hydraulique

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002354864A (ja) * 2001-05-18 2002-12-06 Matsushita Electric Ind Co Ltd リニアコンプレッサ駆動装置
JP2010229870A (ja) * 2009-03-26 2010-10-14 Nissin Kogyo Co Ltd ソレノイドポンプ
JP2014088856A (ja) * 2012-10-31 2014-05-15 Aisin Aw Co Ltd 電磁ポンプ

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4273738B2 (ja) * 2002-10-16 2009-06-03 パナソニック株式会社 リニアコンプレッサ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002354864A (ja) * 2001-05-18 2002-12-06 Matsushita Electric Ind Co Ltd リニアコンプレッサ駆動装置
JP2010229870A (ja) * 2009-03-26 2010-10-14 Nissin Kogyo Co Ltd ソレノイドポンプ
JP2014088856A (ja) * 2012-10-31 2014-05-15 Aisin Aw Co Ltd 電磁ポンプ

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